EP2351937B1 - Hydraulic control system in working machine - Google Patents
Hydraulic control system in working machine Download PDFInfo
- Publication number
- EP2351937B1 EP2351937B1 EP09821710.2A EP09821710A EP2351937B1 EP 2351937 B1 EP2351937 B1 EP 2351937B1 EP 09821710 A EP09821710 A EP 09821710A EP 2351937 B1 EP2351937 B1 EP 2351937B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- flow rate
- accumulator
- oil
- hydraulic
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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Classifications
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
- E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20523—Internal combustion engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/46—Control of flow in the return line, i.e. meter-out control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/47—Flow control in one direction only
- F15B2211/473—Flow control in one direction only without restriction in the reverse direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Description
- The present invention relates to a hydraulic control system in a working machine that can recover and reuse hydraulic energy contained in oil discharged from a hydraulic actuator.
- There exists a working machine, such as a hydraulic shovel, that includes a plurality of hydraulic actuators to which pressurized oil is supplied from a hydraulic pump. A conventional hydraulic circuit of the working machine is configured such that oil discharged from the hydraulic actuators is returned to an oil tank. In the hydraulic shovel, for example, oil discharged from a head-side oil chamber of a boom cylinder is returned to the oil tank when the boom cylinder is retracted to lower a working portion. The oil in the head-side oil chamber of the boom cylinder, which holds a weight of a front working portion, contains high pressure and hydraulic energy. However, the high hydraulic energy is returned to the oil tank without being used further, with a resultant loss of energy. The hydraulic energy contained in the discharged oil from the hydraulic actuator is pressure-accumulated in an accumulator and pressure-accumulated oil in the accumulator is allowed to merge into a discharge passage of a hydraulic pump in order to recover and recycle the hydraulic energy of the discharged oil from the hydraulic actuator (see
Patent Document 1, for example).
Further, the pressure-accumulated oil in the accumulator is allowed to merge into the pump discharge passage with a pressure of the pressure-accumulated oil being unchanged or being increased by a pump motor in accordance with a pressure difference between an accumulated pressure in the accumulator and a discharged pressure from the pump.
WO 2008/007484 A1 shows a hydraulic control system for a working machine, which has a first main pump for drawing oil from an oil tank and discharging it, an accumulator for accumulating under pressure the oil discharged from a head side oil chamber of a boom cylinder when the working section is lowered; and a hybrid pump for drawing the oil accumulated under pressure in the accumulator. The hydraulic control system is constructed such that, when the a boom is lifted, oil discharged from the hybrid pump is supplied to the head side oil chamber and, when the supply flow rate from the hybrid pump is insufficient, the deficiency is supplied to the head side oil chamber from the first main pump.
DE 10 2005 037441 A1 discloses a hydraulic circuit that uses the stored energy from the low energy phase to lower the energy load on the hydraulic pump during the high energy phase. Energy from the hydraulic pump is increased during the low energy phase to increase the amount of stored hydraulic energy. The increased amount of stored energy is then used to intensify or add to the energy generated by the hydraulic pump for the high energy phase.
JP 2008 089024 A - Patent Document 1:
WO 98/13603 - However, a flow rate in the pump discharge passage is likely to increase corresponding to a merging flow rate from the accumulator because the pressure-accumulated oil in the accumulator merges into the discharge passage of the hydraulic pump as disclosed in
Patent Document 1. When a discharge flow rate of the hydraulic pump is not controlled along with a merging flow rate from the accumulator, a pressure of the pump discharge passage increases and a pressure loss also increases in a control valve that controls a supply flow rate of the pressurized oil to the hydraulic actuator, which consumes more energy. Thus, the pressure-accumulated oil in the accumulator cannot efficiently be reused by the above configurations. Further, an operation speed of the hydraulic actuator increases or decreases according to an increase or decrease in the merging flow rate from the accumulator to the hydraulic pump discharge passage. The present invention solves the problems. - The present invention has been made with the object of resolving the above problems in view of the above circumstances, and is solved according to the subject matter of
claim 1. A first exemplary aspect of the present invention provides a hydraulic control system in a working machine that includes an accumulator that pressure-accumulates hydraulic energy contained in oil discharged from a hydraulic actuator; a variable-capacity hydraulic pump that serves as a hydraulic supply source for hydraulic actuators including at least the hydraulic actuator; and a merging oil passage that allows pressure-accumulated oil in the accumulator to merge into oil discharged from the hydraulic pump. The hydraulic control system also includes an accumulator flow rate control valve that controls an accumulator flow rate to be merged from the accumulator into the discharged oil from the hydraulic pump; and a controller that controls the accumulator flow rate control valve and a discharge flow rate of the hydraulic pump. Based on an operation amount of operating members for the hydraulic actuators and a discharge pressure of the hydraulic pump, the controller determines an actuator supply flowrate to be supplied to the hydraulic actuators and controls the hydraulic pump discharge flow rate and the accumulator flow rate so as to supply the actuator supply flow rate corresponding to a total flow rate of the hydraulic pump discharge flow rate and the accumulator flow rate.
A second exemplary aspect of the present invention provides the hydraulic control system in the working machine according to the first aspect, in which the controller includes a contribution proportion setting means that sets, of the actuator supply flow rate to be supplied to the hydraulic actuators, an accumulator contribution proportion to be contributed by the accumulator and a pump contribution proportion to be contributed by the hydraulic pump, and the controller determines the accumulator flow rate to be merged from the accumulator into the discharged oil from the hydraulic pump by multiplying the actuator supply flow rate by the accumulator contribution proportion if an accumulator pressure that is detected by an accumulator pressure detecting means is more than or equal to a predetermined pressure at which the accumulator is allowed to release pressurized oil and if the detected accumulator pressure is more than or equal to the hydraulic pump discharge pressure.
A third exemplary aspect of the present invention provides the hydraulic control system in the working machine according to the first or second aspect, in which the controller controls an opening area of the accumulator flow rate control valve based on a pressure difference between the accumulator pressure and the discharge pressure of the hydraulic pump that are respectively detected by the accumulator pressure detecting means and a pump pressure detecting means so as to compensate the accumulator flow rate to be merged from the accumulator into the oil discharged from the hydraulic pump. - According to the first exemplary aspect of the present invention, the actuator supply flow rate, which is determined based on the operation amount of the hydraulic actuator operating members and the discharged pressure from the hydraulic pump, is allowed to be supplied without an excess or deficiency to the hydraulic actuators by the accumulator flow rate and the discharge flow rate of the hydraulic pump. The pressure-accumulated oil in the accumulator can be used efficiently without being wasted, the discharge flow rate of the hydraulic pump can be reduced, and reliable energy saving can be accomplished.
According to the second exemplary aspect of the present invention, the accumulator flow rate is controlled to contribute a predetermined proportion of the actuator supply flow rate. An easy calculation and control of the accumulator flow rate and an easy discharge flow rate control of the hydraulic pump are thus provided.
According to the third exemplary aspect of the present invention, even when the accumulator pressure and the main pump discharge pressure vary, the accumulator flow rate that merges from the accumulator to the discharged oil from the hydraulic pump can be controlled precisely. The supply flow rate to the hydraulic actuators is thus stabilized and a smooth operation of the hydraulic actuators is achieved. -
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FIG. 1 is a perspective view of a hydraulic shovel; -
FIG. 2 is a hydraulic circuit diagram of a hydraulic control system; -
FIG. 3 is a block diagram showing inputs to and outputs from a controller; and -
FIG. 4 is a block diagram showing a control for an accumulator flow rate and a main pump discharge flow rate. - An embodiment of the present invention will be discussed based on the drawings. In
FIG. 1 , ahydraulic shovel 1, which is an example of a working machine, includes various portions such as a crawler-type lower travelingbody 2; an upper rotatingbody 3 rotatably supported above the lower travelingbody 2; and a working portion 4 fit to a front portion of the upper rotatingbody 3. The working portion 4 includes aboom 5 with a base end portion being supported on the upper rotatingbody 3 to swing up or down; anarm 6 supported on a leading end portion of theboom 5 to swing forward or rearward; and a bucket 7 attached to a leading end portion of thearm 6. - A left and right pair of first and
second boom cylinders boom 5 up and down. The first andsecond boom cylinders side oil chambers boom 5 by pressurized oil supplied to the head-side oil chambers side oil chambers boom 5 by pressurized oil supplied to the rod-side oil chambers side oil chambers boom 5 is raised and lowered. A positional energy possessed by the working portion 4 increases when theboom 5 is raised. The positional energy can be recovered and reused by a hydraulic control system, which will be discussed blow. - The hydraulic control system will be discussed based on a hydraulic circuit diagram as illustrated in
FIG. 2 .Reference numerals reference numeral 10 denotes a variable-capacity main pump (corresponding to a hydraulic pump of the present invention) driven by an engine E installed in thehydraulic shovel 1; reference numeral 11 denotes a pilot pump serving as a pilot hydraulic power source; andreference numeral 12 denotes an oil tank inFIG. 2 . Themain pump 10 serves as a hydraulic supply source for not only the first andsecond boom cylinders hydraulic shovel 1. Nonetheless, only the hydraulic actuators A1 and An among the plurality of hydraulic actuators A1 to An are shown inFIG. 2 . In the present embodiment, thesecond boom cylinder 9 corresponds to a hydraulic actuator of the present invention that pressure-accumulates hydraulic energy contained in discharged oil. The first andsecond boom cylinders - A
regulator 13 controls a discharge flow rate of themain pump 10. Theregulator 13 controls a pump output upon receiving a control signal pressure output from a main pump output controlling solenoid proportionalpressure reducing valve 14 and also performs a constant horsepower control upon receiving a pressure discharged from themain pump 10. Theregulator 13 also performs a flow rate control according to a flow rate control signal pressure Pc output from a main pump flow rate control solenoid proportionalpressure reducing valve 30. Such flow rate control will be discussed later. - A
discharge line 15 of themain pump 10 merges into a mergingoil passage 16 and extends to a pressurized oil supplying oil passage 17. A boomcylinder control valve 18 is connected to the pressurized oil supplying oil passage 17 and performs an oil supply and discharge control over the first andsecond boom cylinders FIG. 2 . - The boom
cylinder control valve 18 is a spool valve that includes raising-side and lowering-side pilot ports pilot ports cylinder control valve 18 is positioned at a neutral position N so as not to allow oil to be supplied to or discharged from the first andsecond boom cylinders side pilot port 18a, the boomcylinder control valve 18 switches to be positioned at a raising-side position X so as to allow pressurized oil in the pressurized oil supplying oil passage 17 to be supplied to the head-side oil chambers second boom cylinders side oil chambers oil tank 12. When a pilot pressure is input to the lowering-side pilot port 18b, the boomcylinder control valve 18 switches to be positioned at a lowering-side position Y so as to allow pressurized oil in the pressurized oil supplying oil passage 17 to be supplied to the rod-side oil chambers second boom cylinders - The head-
side oil chambers second boom cylinders cylinder control valve 18 through first and second head-side oil passages oil passage 21 and a head-sidemain oil passage 22. The first and second head-side oil passages side oil chambers second boom cylinders oil passage 21 connects the head-side oil chamber 8a of thefirst boom cylinder 8 and the head-side oil chamber 9a of thesecond boom cylinder 9 through the first and second head-side oil passages main oil passage 22 connects the head-side communicatingoil passage 21 and the boomcylinder control valve 18. The rod-side oil chambers second boom cylinders cylinder control valve 18 are connected through a rod-side communicatingoil passage 23 and a rod-sidemain oil passage 24. The rod-side communicatingoil passage 23 connects the rod-side oil chamber 8b of thefirst boom cylinder 8 and the rod-side oil chamber 9b of thesecond boom cylinder 9. The rod-sidemain oil passage 24 connects the rod-side communicatingoil passage 23 and the boomcylinder control valve 18. Oil supply and discharge is thus executable between the first andsecond boom cylinders cylinder control valve 18 through the above-mentioned oil passages. - Raising-side and lowering-side solenoid proportional
pressure reducing valves controller 27 so as to output a pilot pressure respectively to the raising-side pilot port 18a and the lowering-side pilot port 18b of the boomcylinder control valve 18. The pilot pressure output from the raising-side and lowering-side solenoid proportionalpressure reducing valves cylinder control valve 18 is controlled to increase or decrease by increasing or decreasing a movement stroke of a spool in response to an increase or decrease in the pilot pressure. - A center
bypass valve passage 18c is formed to the boomcylinder control valve 18. Pressurized oil in the pressurized oil supplying oil passage 17 is allowed to flow into theoil tank 12 when the boomcylinder control valve 18 is positioned at the neutral position N. The centerbypass valve passage 18c is closed, even if a movement stroke of the spool is small, when the boomcylinder control valve 18 switches to be positioned at the raising-side position X or the lowering-side position Y. In addition, the hydraulic actuator control valves C1 to Cn include center bypass valve passages C1c to Cnc similar to the boomcylinder control valve 18. - Based on a control signal from the
controller 27, a main pump flow rate control solenoid proportionalpressure reducing valve 30 outputs a flow rate control signal pressure Pc. After being output from the main pump flow rate control solenoid proportionalpressure reducing valve 30, the flow rate control signal pressure Pc is input into theregulator 13 that performs a discharge flow rate control of themain pump 10. Theregulator 13 controls a discharge flow rate of themain pump 10 to minimize a pump flow rate when the input flow rate control signal pressure Pc is a maximum value and to increase a pump flow rate as the input flow rate control signal pressure Pc decreases. - The first and second head-
side oil passages side oil chambers second boom cylinders second check valves rate control valves side oil passages second check valves side oil chambers side oil chambers rate control valves side oil chambers side oil chambers second boom cylinders second check valves side oil chambers second boom cylinders rate control valves - The first and second flow
rate control valves pilot ports pilot ports rate control valves side oil passages pilot ports rate control valves side oil passages - First and second solenoid proportional
pressure reducing valves controller 27 so as to output a pilot pressure respectively to thepilot ports rate control valves rate control valves pressure reducing valves - First and
second relief valves side oil passages second boom cylinders second relief valves - Disposed to the head-side communicating
oil passage 21, which connects the head-side oil chambers second boom cylinders side oil passages valve 39 that opens or closes the head-side communicatingoil passage 21 based on a control signal from thecontroller 27. The head-side oil chambers second boom cylinders side oil passages valve 39 is positioned at an open position X to open the head-side communicatingoil passage 21. The head-side oil chambers second boom cylinders valve 39 is positioned at a closing position N to close the head-side communicatingoil passage 21. The rod-side oil chambers second boom cylinders valve 39 is not disposed to the rod-side communicatingoil passage 23. - A head-side
oil discharge passage 40 extends to theoil tank 12 from the first head-side oil passage 19. An unloadvalve 41 is disposed to the head-sideoil discharge passage 40. - The unload
valve 41 includes apoppet valve 42 and an unload valvesolenoid switching valve 43. The unload valvesolenoid switching valve 43 is switchable from an OFF position N to an ON position X based on a control signal output from thecontroller 27. When the unload valvesolenoid switching valve 43 is positioned at an OFF position N, the unloadvalve 41 stays closed to prevent an oil flow from the first head-side oil passage 19 to theoil tank 12, i.e., to close the head-sideoil discharge passage 40. When the unload valvesolenoid switching valve 43 switches to be positioned at an ON position X, the unloadvalve 41 is open to allow for an oil flow from the first head-side oil passage 19 to theoil tank 12, i.e., to open the head-sideoil discharge passage 40. The open state of the unloadvalve 41 caused by positioning the unload valvesolenoid switching valve 43 at the ON position X thus allows pressurized oil in the head-side oil chamber 8a of thefirst boom cylinder 8 to flow into theoil tank 12 through the first flowrate control valve 33 and the head-sideoil discharge passage 40. - The pressurized oil in the head-
side oil chamber 8a of thefirst boom cylinder 8 is allowed to flow into theoil tank 12 through the first flowrate control valve 33 and the head-sideoil discharge passage 40 when the unloadvalve 41 is open. In this case, maximizing an opening area of the first flowrate control valve 33 enables the pressurized oil in the head-side oil chamber 8a of thefirst boom cylinder 8 to flow into theoil tank 12 in a substantially unloaded state. - A
recovery oil passage 44 is connected to the second head-side oil passage 20. Supplied to therecovery oil passage 44 is oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 through the second head-side oil passage 20. Therecovery oil passage 44 is also connected to anaccumulator oil passage 45 through a cylinder-side check valve 46 and an accumulator-side check valve 49 as discussed below. Theaccumulator oil passage 45 is connected to anaccumulator 59 to supply and discharge pressurized oil to and from theaccumulator 59. - The cylinder-
side check valve 46 includes apoppet valve 47 and a cylinder-side check valvesolenoid switching valve 48. The cylinder-side check valvesolenoid switching valve 48 is switchable from an OFF position N to an ON position X based on a control signal output from thecontroller 27. The cylinder-side check valve 46 stays closed to prevent an oil flow from therecovery oil passage 44 to theaccumulator oil passage 45 when the cylinder-side check valvesolenoid switching valve 48 is positioned at an OFF position N. When the cylinder-side check valvesolenoid switching valve 48 switches to be positioned at an ON position X, the cylinder-side check valve 46 is open to allow for a bidirectional flow between therecovery oil passage 44 and theaccumulator oil passage 45. - The accumulator-
side check valve 49 includes apoppet valve 50 and an accumulator-side check valvesolenoid switching valve 51. The accumulator-side check valvesolenoid switching valve 51 is switchable from an OFF position N to an ON position X based on a control signal output from thecontroller 27. The accumulator-side check valve 49 stays closed to prevent an oil flow from theaccumulator oil passage 45 to therecovery oil passage 44 when the accumulator-side check valvesolenoid switching valve 51 is positioned at an OFF position N. When the accumulator-side check valvesolenoid switching valve 51 switches to be positioned at an ON position X, the accumulator-side check valve 49 is open to allow for a bidirectional flow between therecovery oil passage 44 and theaccumulator oil passage 45. The accumulator-side check valve 49 allows for an oil flow from therecovery oil passage 44 to theaccumulator oil passage 45 even when the accumulator-side check valvesolenoid switching valve 51 is positioned at the OFF position N. When the accumulator-side check valvesolenoid switching valve 51 is positioned at the ON position X, oil is allowed to flow from therecovery oil passage 44 to theaccumulator oil passage 45 by losing little pressure because no pressure in theaccumulator oil passage 45 is applied to aspring chamber 50a of thepoppet valve 50. - Oil is prevented from flowing from the
recovery oil passage 44 to theaccumulator oil passage 45 and from theaccumulator oil passage 45 to therecovery oil passage 44 when both the cylinder-side check valve 46 and the accumulator-side check valve 49 stay closed. Oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 can be pressure-accumulated in theaccumulator 59 through therecovery oil passage 44 and theaccumulator oil passage 45 when both the cylinder-side check valve 46 and the accumulator-side check valve 49 are open. Theaccumulator 59 of the present embodiment is an optimal bladder type accumulator for storing hydraulic energy, but is not restricted thereto and may be a piston type, for example. - The merging
oil passage 16 extends from theaccumulator oil passage 45 to thedischarge line 15 of themain pump 10. An accumulator flowrate control valve 52 is disposed to the mergingoil passage 16. - A spool of the accumulator flow
rate control valve 52 moves based on an operation of an accumulator flow rate control valve electro-hydraulic conversion valve 53 into which a control signal is input from thecontroller 27. When the accumulator flow rate control valve electro-hydraulic conversion valve 53 is unoperated, the accumulator flowrate control valve 52 is positioned at a closed state N to close the mergingoil passage 16. A movement of the spool by an operation of the accumulator flow rate control valve electro-hydraulic conversion valve 53 causes the accumulator flowrate control valve 52 to switch to be positioned at an open position X to open the mergingoil passage 16. Acheck valve 54 is integrated into the accumulator flowrate control valve 52. Thecheck valve 54 allows for an oil flow from theaccumulator oil passage 45 to thedischarge line 15 and prevents an oil flow in a reverse direction thereof. When the accumulator flowrate control valve 52 switches to be positioned at the open position X, pressurized oil that is pressure-accumulated in theaccumulator 59 is allowed to merge into thedischarge line 15 of themain pump 10 through theaccumulator oil passage 45 and the mergingoil passage 16. - An opening area of the accumulator flow
rate control valve 52 is controlled to increase or decrease according to a signal value of a control signal input from thecontroller 27 to the accumulator flow rate control valve electro-hydraulic conversion valve 53. The opening area of the accumulator flowrate control valve 52 controls an accumulator flow rate that merges from theaccumulator 59 into thedischarge line 15 of themain pump 10 through the mergingoil passage 16, which will be discussed more later. - The
controller 27, which includes a microcomputer, etc., inputs signals from a boomoperation detecting means 60, a pump pressure sensor (corresponding to a pump pressure detecting means of the present invention) 61, a first head-side pressure sensor 62, a second head-side pressure sensor 63, an accumulator pressure sensor (corresponding to an accumulator pressure detecting means of the present invention) 64, hydraulic actuator operation detecting means 65a to 65n and so on as illustrated in a block diagram ofFIG. 3 . The boomoperation detecting means 60 detects an operation direction and amount of the boom operating lever. Thepump pressure sensor 61 detects a pressure of themain pump 10. The first head-side pressure sensor 62 detects a pressure of the head-side oil chamber 8a of thefirst boom cylinder 8. The second head-side pressure sensor 63 detects a pressure of the head-side oil chamber 9a of thesecond boom cylinder 9. Theaccumulator pressure sensor 64 detects a pressure of theaccumulator 59. The hydraulic actuator operation detecting means 65a to 65n detect an operation direction and amount of operating members (not shown) for the hydraulic actuators A1 to An. Based on the input signals, thecontroller 27 outputs control signals to the raising-side solenoid proportionalpressure reducing valve 25, the lowering-side solenoid proportionalpressure reducing valve 26, the main pump flow rate control solenoid proportionalpressure reducing valve 30, the first solenoid proportionalpressure reducing valve 35, the second solenoid proportionalpressure reducing valve 36, the head-side communicating passage opening and closingvalve 39, the unload valvesolenoid switching valve 43, the cylinder-side check valvesolenoid switching valve 48, the accumulator-side check valvesolenoid switching valve 51, the accumulator flow rate control valve electro-hydraulic conversion valve 53 and so on. - A bilateral and unilateral holding control will first be discussed before other controls performed by the
controller 27. Based on a boom operating lever operation signal input from the boomoperation detecting means 60, thecontroller 27 judges to perform a bilateral holding control so as to hold a weight of the working portion 4 by a pressure of the head-side oil chambers second boom cylinders operation detecting means 60, thecontroller 27 judges to perform a unilateral holding control so as to hold a weight of the working portion 4 by a pressure of the head-side oil chamber 9a of thesecond boom cylinder 9 when the boom operating lever is operated to a lowering side, i.e., when the working portion 4 is lowered. - Judging to perform the bilateral holding control, the
controller 27 outputs a control signal to the unload valvesolenoid switching valve 43 to be positioned at an OFF position N so as to close the unloadvalve 41. Oil in the head-side oil chamber 8a of thefirst boom cylinder 8 is thus prevented from flowing into theoil tank 12 through the head-sideoil discharge passage 40. Thecontroller 27 also outputs a control signal to the head-side communicating oil passage opening and closingvalve 39 to be positioned at an open position X. The head-side oil chambers second boom cylinders side oil passages second boom cylinders side oil chambers second boom cylinders - Judging to perform the unilateral holding control, the
controller 27 outputs a control signal to the head-side communicating oil passage opening and closingvalve 39 to be positioned at a closed position N. The head-side oil chambers second boom cylinders controller 27 also outputs a control signal for a maximum pilot pressure output to the first solenoid proportionalpressure reducing valve 35 so as to maximize an opening area of the first flowrate control valve 33. Thecontroller 27 also outputs a control signal to the unload valvesolenoid switching valve 43 to be positioned at an ON position X so as to open the unloadvalve 41. Oil in the head-side oil chamber 8a of thefirst boom cylinder 8 thus flows into theoil tank 12 through the first head-side oil passage 19 and the head-sideoil discharge passage 40, which in return decreases a pressure of the head-side oil chamber 8a of thefirst boom cylinder 8 down to substantially a pressure of theoil tank 12. In this state, the weight of the working portion 4 is not held by thefirst boom cylinder 8, and only thesecond boom cylinder 9 is involved in holding the weight of working portion 4. The unilateral holding control is thus performed to hold the weight of the working portion 4 by the pressure of the head-side oil chamber 9a of thesecond boom cylinder 9, which is one of the first andsecond boom cylinders side oil chamber 9a of thesecond boom cylinder 9 in the unilateral holding control rises approximately twice as much as the pressure of the head-side oil chambers second boom cylinders - Controls by the
controller 27 will now be discussed in connection with operations of the boom operating lever.
Thecontroller 27 outputs no pilot pressure output control signal to the raising-side solenoid proportionalpressure reducing valve 25, the lowering-side solenoid proportionalpressure reducing valve 26, the first solenoid proportionalpressure reducing valve 35 and the second solenoid proportionalpressure reducing valve 36 when the boom operating lever is unoperated to both boom lowering and raising sides, i.e., a raising and lowering operation of the working portion 4 is stopped. The boomcylinder control valve 18 is thus positioned at a neutral position N, and also the first and second flowrate control valves solenoid switching valve 48 and the accumulator-side check valvesolenoid switching valve 51 are controlled to be positioned at an OFF position N, which in return allows both the cylinder-side check valve 46 and the accumulator-side check valve 49 to stay closed. Further, an operation signal is not output to the accumulator flow rate control valve electro-hydraulic conversion valve 53, which in return allows the accumulator flowrate control valve 52 to be positioned at a closed position N. Further, the control is performed such that the head-side communicating oil passage opening and closingvalve 39 is positioned at an open position X and the unloadvalve 41 is closed because of the bilateral holding control when the raising and lowering operation of the working portion 4 is stopped as discussed above. Further, the main pump flow rate control solenoid proportionalpressure reducing valve 30 is controlled to output a maximum value of the flow rate control signal pressure Pc to theregulator 13. Themain pump 10 is thus controlled to operate at a minimum pump flow rate. - On the other hand, another control is performed such that the head-side communicating oil passage opening and closing
valve 39 is positioned at a closed position N, an opening area of the first flowrate control valve 33 is maximized, and the unloadvalve 41 is open because of the unilateral holding control when the boom operating lever is operated to a boom lowering side, i.e., the working portion 4 is lowered, as discussed above. Oil discharged from the head-side oil chamber 8a of thefirst boom cylinder 8 thus flows into theoil tank 12 through the head-sideoil discharge passage 40, and the weight of the working portion 4 is held by the pressure of the head-side oil chamber 9a of thesecond boom cylinder 9. - When the boom operating lever is operated to the boom lowering side, the
controller 27 outputs a control signal to the lowering-side solenoid proportionalpressure reducing valve 26 to output a pilot pressure corresponding to an amount of the operation of the boom operating lever to the lowering-side pilot port 18b of the boomcylinder control valve 18. The boomcylinder control valve 18 thus switches to be positioned at a lowering-side position Y. Pressurized oil in the pressurized oil supplying oil passage 17 is supplied to the rod-side oil chambers second boom cylinders cylinder control valve 18 at the lowering-side position Y, the rod-sidemain oil passage 24 and the rod-side communicatingoil passage 23. - When the boom operating lever is operated to the boom lowering side, the
controller 27 also outputs a control signal to the second solenoid proportionalpressure reducing valve 36 to output a pilot pressure corresponding to the operation amount of the boom operating lever to thepilot port 34a of the second flowrate control valve 34. The second flowrate control valve 34 thus switches to be positioned at an open position X so as to open the second head-side oil passage 20. Pressurized oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 is supplied to therecovery oil passage 44 through the second flowrate control valve 34 at the open position X. A flow rate of the pressurized oil is controlled by an opening area of the second flowrate control valve 34. Compared with the bilateral holding control, the pressure of the oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 is approximately twice as much because of the unilateral holding control where the working portion 4 is lowered and the weight of the working portion 4 is held by the head-side oil chamber 9a of thesecond boom cylinder 9, as discussed above. The high-pressure oil is supplied to therecovery oil passage 44. - When the boom operating lever is operated to the boom lowering side, the
controller 27 also outputs a control signal to the cylinder-side check valvesolenoid switching valve 48 and the accumulator-side check valvesolenoid switching valve 51 to switch to be positioned at an ON position X. Both the cylinder-side check valve 46 and the accumulator-side check valve 49 are thus open to allow for an oil flow from therecovery oil passage 44 to theaccumulator oil passage 45. The oil, which is discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 and supplied to therecovery oil passage 44, flows into theaccumulator oil passage 45 to be pressure-accumulated in theaccumulator 59 through theaccumulator oil passage 45. - In other words, when the working portion 4 is lowered, the unilateral holding control is performed to hold the weight of the working portion 4 by the pressure of the head-
side oil chamber 9a of thesecond boom cylinder 9, and the oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 is pressure-accumulated in theaccumulator 59. The pressure of the head-side oil chamber 9a of thesecond boom cylinder 9 is approximately twice as much as the pressure in the bilateral holding control. Pressure-accumulated in theaccumulator 59 is thus pressurized oil high enough for heavy load work such as excavation work, lifting and rotation, and so on. - When the boom operating lever is operated to the boom lowering side, the
controller 27 outputs no operation signal to the accumulator flow rate control valve electro-hydraulic conversion valve 53. The accumulator flowrate control valve 52 is thus controlled to be positioned at a closed position N to close the mergingoil passage 16. Pressurized oil is not supplied from theaccumulator oil passage 45 through the mergingoil passage 16 to the pressurized oil supplying passage 17. Only oil discharged from themain pump 10 is supplied to the pressurized oil supplying passage 17. - When the boom operating lever is operated to the boom lowering side, the
controller 27 also outputs a control signal to the main pump flow rate control solenoid proportionalpressure reducing valve 30 to output a flow rate control signal pressure Pc to theregulator 13 so as to set a discharge flow rate of themain pump 10 to be a flow rate calculated by a pump flowrate calculating portion 71. The discharge flow rate of themain pump 10 is thus controlled to correspond to the flow rate calculated by the pump flowrate calculating portion 71. Such main pump discharge flow rate control will be discussed more later. - Another control will now be discussed in which the boom operating lever is operated to the boom raising side, i.e., the working portion 4 is raised. The control is performed such that the head-side communicating oil passage opening and closing
valve 39 is positioned at an open position X and the unloadvalve 41 is closed because of the bilateral holding control when the working portion 4 is raised, as discussed above. - When the boom operating lever is operated to the boom raising side, the
controller 27 outputs a control signal to the raising-side solenoid proportionalpressure reducing valve 25 to output a pilot pressure corresponding to an amount of the operation of the boom operating lever to the raising-side pilot port 18a of the boomcylinder control valve 18. The boomcylinder control valve 18 switches to be positioned at a raising-side position X. Pressurized oil in the pressurized oil supplying oil passage 17 is supplied to the head-side oil chambers second boom cylinders cylinder control valve 18 at the raising-side position X. Oil discharged from the rod-side oil chambers oil tank 12. - In the above case, the
controller 27 outputs no pilot pressure output control signal to the first and second solenoid proportionalpressure reducing valves rate control valves valve 39 is positioned at the open position X, and the unloadvalve 41 is closed. The pressurized oil, which is supplied to the head-side oil chambers second boom cylinders cylinder control valve 18 at the raising-side position X, reaches to the head-side oil chambers second boom cylinders main oil passage 22, the head-side communicatingoil passage 21 and the first andsecond check valves side oil passages oil tank 12 through the head-sideoil discharge passage 40. - When the boom operating lever is operated to the boom raising side, the
controller 27 also controls the cylinder-side check valvesolenoid switching valve 48 and the accumulator-side check valvesolenoid switching valve 51 to be positioned at an OFF position N. The cylinder-side check valve 46 and the accumulator-side check valve 49 thus stay closed, and therecovery oil passage 44 and theaccumulator oil passage 45 are blocked from each other. - When the boom operating lever is operated to the boom raising side, the
controller 27 also outputs an operation signal to the accumulator flow rate control valve electro-hydraulic conversion valve 53 to switch the accumulator flowrate control valve 52 to be positioned at an open position X. The accumulator flowrate control valve 52 thus opens the mergingoil passage 16 that extends from theaccumulator oil passage 45 to thedischarge line 15 of themain pump 10. Pressurized oil that is pressure-accumulated in theaccumulator 59 merges into thedischarge line 15 of themain pump 10 through theaccumulator oil passage 45 and the mergingoil passage 16 and is further supplied to the head-side oil chambers second boom cylinders cylinder control valve 18 at the raising-side position X. In this case, an accumulator merging flow rate from theaccumulator 59 to thedischarge line 15 of themain pump 10 is controlled by an opening area of the accumulator flowrate control valve 52. Such accumulator flow rate control will be discussed more later. - When the boom operating lever is operated to the boom raising side, the
controller 27 also outputs a control signal to the main pump flow rate control solenoid proportionalpressure reducing valve 30 to output a flow rate control signal pressure Pc to theregulator 13 so as to set a discharge flow rate of themain pump 10 to be a flow rate calculated by the pump flowrate calculating portion 71. The discharge flow rate of themain pump 10 is thus controlled to correspond to the flow rate calculated by the pump flowrate calculating portion 71. Such main pump discharge flow rate control will be discussed more later. - In other words, when the working portion 4 is raised, pressure-accumulated oil in the
accumulator 59 merges into oil discharged from themain pump 10 through the mergingoil passage 16. The merging pressurized oil is supplied to the head-side oil chambers second boom cylinders cylinder control valve 18 at the raising-side position X. The hydraulic energy, which is recovered in theaccumulator 59 when the working portion 4 is lowered, can thus be reused when the working portion 4 is raised. - Pressure-accumulated oil in the
accumulator 59 can be used for pressurized oil to be supplied to not only the first andsecond boom cylinders main pump 10 by positioning the accumulator flowrate control valve 52 at an open position X to allow the pressure-accumulated oil in theaccumulator 59 to merge into oil discharged from themain pump 10 when operating members of the hydraulic actuators A1 to An, the hydraulic supply source of which is themain pump 10, are operated or when a boom raising-side operation of the boom operating lever is performed in conjunction with the operating members of the hydraulic actuator A1 to An. In this case, the high-pressure oil is pressure-accumulated in theaccumulator 59 as discussed above, which can be applied to various operations including heavy loads such as excavation work and lifting and rotation. - Discussed now with reference to a block diagram as illustrated in
FIG. 4 will be the accumulator flow rate control (a merging flow rate from theaccumulator 59 to thedischarge line 15 of the main pump 10) for merging the pressure-accumulated oil in theaccumulator 59 into the oil discharged from themain pump 10 and the discharge flow rate control of themain pump 10. In order to carry out the controls, thecontroller 27 first calculates a flow rate to be supplied to the hydraulic actuators (first andsecond boom cylinders - When the actuator supply flow rate Qc is calculated, the
controller 27 first inputs detection signals, which are input from the boomoperation detecting means 60 and the hydraulic actuator operation detecting means 65a to 65n, to an operation demand flowrate calculating portion 67. The operation demand flowrate calculating portion 67 includes a table that indicates a relationship between an operation amount L of each operating member of the hydraulic actuators and an operation demand flow rate Qr that is set according to the operation amount L of the hydraulic actuator operating members. The operation demand flowrate calculating portion 67 uses the table to determine the operation demand flow rate Qr of the respective hydraulic actuators. The operation demand flow rate Qr of the respective hydraulic actuators, which is determined by the operation demand flowrate calculating portion 67, is then summed by anadder 68 and output as a total operation demand flow rate Qsum (Qsum = Qr + Qr··· + Qr) to an actuator supply flowrate calculating portion 69. - The actuator supply flow
rate calculating portion 69 inputs the total operation demand flow rate Qsum, the detection signal of thepump pressure sensor 61 and a pump output signal Pw. The pump output signal Pw, which adjusts an output of themain pump 10 according to an output of the engine E, detailed work, etc., is set according to a dial value of an accelerator dial that sets a non-load rotation speed of the engine E, for example. A pump constant horsepower curve (P-Q curve) indicates a relationship between a pump discharge pressure P and a pump flow rate Q for performing a constant horsepower control. The P-Q curve is set in advance according to a signal value of the pump output signal Pw. The actuator supply flowrate calculating portion 69 determines a pump flow rate Qd on the pump constant horsepower curve according to the pump constant horsepower curve to be determined by the pump output signal Pw and a discharge pressure Pp of themain pump 10 to be input from thepump pressure sensor 61. The actuator supply flowrate calculating portion 69 also determines a smallest value by comparison among the pump flow rate Qd on the pump constant horsepower curve, the total operation demand flow rate Qsum and a maximum flow rate Qmax of themain pump 10, and then outputs the smallest value among the compared values as a actuator supply flow rate Qc to be supplied to the hydraulic actuators that are operated with the operating members. - The actuator supply flow rate Qc, which is output from the actuator supply flow
rate calculating portion 69, is input to an accumulator flowrate calculating portion 70 to be used for calculating an accumulator flow rate Qa and simultaneously input to the pump flowrate calculating portion 71 to be used for calculating a discharge flow rate Qp of themain pump 10. - A calculation of the accumulator flow rate Qa made in the accumulator flow
rate calculating portion 70 will now be discussed. The actuator supply flow rate Qc, which is output from the actuator supply flowrate calculating portion 69, multiplied by an accumulator contribution portion Ra that is set by a contribution proportion setting portion (corresponding to a contribution proportion setting means of the present invention) 72 equals the accumulator flow rate Qa that merges from theaccumulator 59 into the oil discharged from the main pump 10 (i.e., Qa = Qc * Ra). The calculation of the accumulator flow rate Qa is performed if a pressure Pa of theaccumulator 59 that is input from theaccumulator pressure sensor 64 is more than or equal to a pressure Pas that is set in advance to allow theaccumulator 59 to release pressurized oil (Pa ≥ Pas) and if the pressure Pa of theaccumulator 59 is more than or equal to the discharge pressure Pp of the main pump 10 (Pa ≥ Pp). If the pressure Pa of theaccumulator 59 is less than the set pressure Pas or the discharge pressure Pp of themain pump 10, then pressure-accumulated oil in theaccumulator 59 is not allowed to merge into themain pump 10. In this case, the accumulator flow rate Qa is calculated as "zero". In addition, the accumulator flow rate Qa is calculated as "zero" when the boom operating lever is operated to the boom lowering side because the pressure-accumulation is performed by theaccumulator 59 as discussed above. - Of the actuator supply flow rate Qc, which is supplied to the hydraulic actuators, the contribution
proportion setting portion 72 sets the accumulator contribution proportion Ra (0 < Ra ≤1) to be contributed by theaccumulator 59 and the pump contribution proportion Rp (Rp = 1 - Ra) to be contributed by themain pump 10. For example, if the accumulator contribution proportion Ra is set to be 0.5 (Ra = 0.5) and the pump contribution proportion Rp is set to be 0.5 (Rp = 0.5), then a supply flow rate to the hydraulic actuators is contributed fifty-fifty by theaccumulator 59 and themain pump 10. The accumulator contribution proportion Ra and the pump contribution proportion Rp, which is set in the contributionproportion setting portion 72, can be set arbitrarily according to, for example, a capacity of theaccumulator 59 by using such an operation means as an operation panel to be connected to thecontroller 27. - The
controller 27 also outputs a control signal to the accumulator flow rate control valve electro-hydraulic conversion valve 53 to control an opening area of the accumulator flowrate control valve 52 such that the accumulator flow rate Qa, which is calculated in the accumulator flowrate calculating portion 70, is allowed to merge from theaccumulator 59 into the oil discharged from themain pump 10. In this case, the opening area of the accumulator flowrate control valve 52 is controlled such that the following Formula I is satisfied:rate calculating portion 70; C represents a coefficient; A represents the opening area of the accumulator flowrate control valve 52; Pa represents the pressure of theaccumulator 59; and Pp represents the discharge pressure of themain pump 10. - The opening area of the accumulator
flow control valve 52 is controlled to change according to a pressure difference between the pressure Pa of theaccumulator 59 and the discharge pressure Pp of themain pump 10. The accumulator flow rate Qa, which is calculated in the accumulator flowrate calculating portion 70, can thus be compensated even if the pressure Pa of theaccumulator 59 and the discharge pressure Pp of themain pump 10 vary. In addition, when the accumulator flow rate Qa is calculated to be "zero" (Qa = 0) in the accumulator flowrate calculating portion 70, the accumulator flowrate control valve 52 is controlled to be positioned at a closed position N to close the mergingoil passage 16. - A calculation of the discharge flow rate Qp of the
main pump 10 made in the pump flowrate calculating portion 71 will now be discussed. The pump flowrate calculating portion 71 calculates the discharge flow rate Qp of themain pump 10 by subtracting the accumulator flow rate Qa, which is calculated in the accumulator flowrate calculating portion 70, from the actuator supply flow rate Qc, which is output from the actuator supply flow rate calculating portion 69 (i.e., Qp = Qc - Qa). The calculation is thus performed such that a total flow rate of the discharge flow rate Qp of themain pump 10 and the accumulator flow rate Qa corresponds to the actuator supply flow rate Qc that is supplied to the hydraulic actuators. In addition, when the accumulator flow rate Qa is "zero", the discharge flow rate Qp of themain pump 10 corresponds to the actuator supply flow rate Qc. - The
controller 27 outputs a control signal to the main pump flow rate control solenoid proportionalpressure reducing valve 30 to output a flow rate control signal pressure Pc to theregulator 13 in order to allow a discharge flow rate of themain pump 10 to correspond to the discharge flow rate Qp that is calculated in the pump flowrate calculating portion 71. The discharge flow rate of themain pump 10 is thus controlled to correspond to the discharge flow rate Qp that is calculated in the pump flowrate calculating portion 71. - In the present embodiment arranged as discussed above, the unilateral holding control is performed to hold the weight of the working portion 4 by only the head-
side oil chamber 9a of thesecond boom cylinder 9 when the working portion 4 is lowered. In doing so, the oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9, which holds the weight of the working portion 4, is pressure-accumulated in theaccumulator 59. The high-pressure pressurized oil is pressure-accumulated in theaccumulator 59, which can be utilized for heavy load operations. Further, the pressure-accumulated pressurized oil in theaccumulator 59 is allowed to merge into the oil discharged from themain pump 10 through the mergingoil passage 16. The hydraulic energy, which is contained in the oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9, can thus be utilized for the pressurized oil to be supplied to the first andsecond boom cylinders accumulator 59 to the oil discharged from themain pump 10 is controlled by the accumulator flowrate control valve 52 that is disposed to the mergingoil passage 16. Based on an operation amount of the boom operating lever and the operating members for the hydraulic actuators and the discharge pressure Pp of themain pump 10, thecontroller 27, which controls the accumulator flowrate control valve 52 and the discharge flow rate of themain pump 10, determines the actuator supply flow rate Qc to be supplied to the hydraulic actuators (first andsecond boom cylinders controller 27 then controls the discharge flow rate of themain pump 10 and the accumulator flow rate in order to supply the actuator supply flow rate Qc as the total flow rate of the discharge flow rate Qp of themain pump 10 and the accumulator flow rate Qa. - The actuator supply flow rate Qc, which is determined based on the operation amount of the hydraulic actuator operating members and the discharge pressure Pp of the
main pump 10, is allowed to be supplied without an excess and deficiency by the accumulator flow rate Qa and the discharge flow rate Qp of themain pump 10 into the pressurized oil supplying oil passage 17 that supplies the pressurized oil to the first andsecond boom cylinders accumulator 59 is used by merging into the oil discharged from thehydraulic pump 10, the pressure-accumulated oil in theaccumulator 59 can be used efficiently without being wasted, i.e., without increasing a pressure loss in the control valves (the boomcylinder control valve 18 and the hydraulic actuator control valves C1 to Cn) or without varying an operation speed of the hydraulic actuators according to an increase or decrease in the total flow rate from theaccumulator 59. In doing so, the discharge flow rate of themain pump 10 can thus be reduced, and a reliable energy saving is also secured. - Further in the present embodiment arranged as discussed above, the
controller 27 includes the contributionproportion setting portion 72 that sets the accumulator contribution proportion Ra and the pump contribution proportion Rp of the actuator supply flow rate Qc. The accumulator contribution proportion Ra is contributed by theaccumulator 59, the pump contribution proportion Rp is contributed by themain pump 10, and the actuator supply flow rate Qc is supplied to the hydraulic actuators (the first andsecond boom cylinders controller 27 determines the accumulator flow rate Qa, which merges from theaccumulator 59 into oil discharged from themain pump 10, if the accumulator pressure Pa, which is detected by theaccumulator pressure sensor 64, is more than or equal to the set pressure Pas, which is set in advance as the pressure at which theaccumulator 59 is allowed to release pressurized oil (i.e., Pa ≥ Pas) and if the accumulator pressure Pa is more than or equal to the discharge pressure Pp of the main pump 10 (i.e., Pa ≥ Pp). The accumulator flow rate Qa is thus controlled to contribute a predetermined proportion of the actuator supply flow rate Qc without being affected by the pressure Pa of theaccumulator 59 or the discharge pressure Pp of themain pump 10. The accumulator flow rate Qa is easily calculated and controlled, and the discharge rate control of themain pump 10 is also easily performed. In addition, if the accumulator pressure Pa is less than the set pressure Pas or the discharge pressure Pp of themain pump 10, or when a pressure accumulation of theaccumulator 59 is performed, i.e., when oil is not allowed to merge from theaccumulator 59 into oil discharged from themain pump 10, then the accumulator flow rate Qa is calculated to be "zero", in which a total flow rate of the actuator supply flow rate Qc is supplied by the discharge flow rate Qp of themain pump 10. - Further in the present embodiment arranged as discussed above, the accumulator flow rate Qa is controlled accurately to be what is calculated by the accumulator flow
rate calculating portion 70 even if there exists variation in the pressure Pa of theaccumulator 59 or the discharge pressure Pp of themain pump 10, because thecontroller 27 controls an opening area of the accumulatorflow control valve 52 based on a pressure difference between the pressure Pa of theaccumulator 59 and the discharge pressure of thehydraulic pump 10 in order to compensate the accumulator flow rate Qa. A stable supply flow rate to the hydraulic actuators and a smooth operation of the hydraulic actuators are achieved. - Of course, the present invention will not be restricted to the embodiment arranged as discussed above. In the above embodiment, an opening area of the boom
cylinder control valve 18 is controlled to increase or decrease in accordance with an operation amount of the boom operating lever, for example. However, another control may also be carried out such that an opening area of the boomcylinder control valve 18 is allowed to fully open regardless of an operation amount of a boom operating lever when only the boom operating lever is operated among the operating members of the hydraulic actuators whose hydraulic supply source is themain pump 10. In other words, a supply flow rate with respect to the first andsecond boom cylinders second boom cylinders cylinder control valve 18. It is because the accumulator flow rate Qa and the discharge flow rate Qp of themain pump 10 are controlled such that the actuator supply flow rate Qc, which is determined by thecontroller 27, is supplied to the first andsecond boom cylinders cylinder control valve 18 to fully open, enables a reduced pressure loss in a passage through the boomcylinder control valve 18. - Further, the boom
cylinder control valve 18 includes the centerbypass valve passage 18c that allows pressurized oil in the pressurized oil supplying oil passage 17 to flow into theoil tank 12 when the boomcylinder control valve 18 is positioned at a neutral position N. The centerbypass valve passage 18c is set to be closed even if a movement stroke of the spool is small when the boomcylinder control valve 18 switches to be positioned at a raising-side position X or a lowering-side position Y. The hydraulic actuator control valves C1 to Cn also include the center bypass valve passages C1c to Cnc similar to the centerbypass valve passage 18c of the boomcylinder control valve 18. Discharged oil from themain pump 10 is thus allowed to flow at a minimum flow rate into theoil tank 12 through the centerbypass valve passages 18c and C1c to Cnc when all the hydraulic actuators, the hydraulic supply source of which is themain pump 10, are unoperated. An oil loss by flowing into theoil tank 12 through the centerbypass valve passages 18c and C1c to C1nc can be eliminated because the centerbypass valve passages 18c and C1c to Cnc are closed when the hydraulic actuators are operated. Instead of using the above center bypass valve passages, however, the present invention can also be carried out by using control valves (boom cylinder control valve and other hydraulic actuator control valves) that include center bypass valve passages in which an opening amount thereof is set to be smaller when a movement stroke of the spool is greater. In this case, a discharge flow rate Qp of themain pump 10 is determined by adding a center bypass flow rate Qby (flow rate into theoil tank 12 through the center bypass valve passages) to a flow rate obtained by subtracting an accumulator flow rate Qa from an actuator supply flow rate Qc (i.e., Qp = Qc - Qa + Qby). The actuator supply flow rate Qc and the accumulator flow rate Qa can be determined in the same manner as in the aforementioned embodiment. The center bypass flow rate Qby can be determined using the following Formula II: - Further, when the working portion 4 is lowered, the total amount of the discharged oil from the head-
side oil chamber 9a of thesecond boom cylinder 9 is pressure-accumulated in theaccumulator 59, and the pressurized oil is not allowed to flow from theaccumulator oil passage 45 into the pressurized oil supplying oil passage 17, because the accumulator flowrate control valve 52 is positioned at the closed position N to close the mergingoil passage 16. Alternatively, the accumulator flowrate control valve 52 can be configured to be positioned at an open position X to open the mergingoil passage 16 when the working portion 4 is lowered, which in return allows a portion of oil discharged from the head-side oil chamber 9a of thesecond boom cylinder 9 to merge into oil discharged from themain pump 10. In this case, the discharged oil from the head-side oil chamber 9a of thesecond boom cylinder 9 is pressure-accumulated in theaccumulator 59 and simultaneously recycled so as to be supplied to the rod-side oil chambers second boom cylinders oil passage 16, the pressurized oil supplying oil passage 17 and the boomcylinder control valve 18 at the lowering-side position Y. Such recycled flow rate can be controlled by an opening area of the accumulator flowrate control valve 52, and a discharge flow rate of themain pump 10 can be controlled by the recycled flow rate. Theaccumulator 59 can be downsized because the portion of the discharged oil from the head-side oil chamber 9a of thesecond boom cylinder 9 can be used as the recycled oil. The recycled oil can also be used for pressurized oil to be supplied to the hydraulic actuators A1 to An because the recycled oil is allowed to merge into the discharged oil from themain pump 10. - Further, the weight of the working portion 4 is held when the working portion 4 is raised or not both raised and lowered by using the pressure of the head-
side oil chambers second boom cylinders side oil chamber 9a of thesecond boom cylinder 9 and the discharged oil from the head-side oil chamber 9a of thesecond boom cylinder 9 is pressure-accumulated in theaccumulator 59. The high-pressure pressurized oil can thus be pressure-accumulated in theaccumulator 59, which can be applied to various heavy load works. However, the present invention is not restricted to the above configuration and indeed can also be carried out to provide a hydraulic control system for various working machines that include an accumulator that stores hydraulic energy contained in oil discharged from a hydraulic actuator; and a merging oil passage that allows the stored oil in the accumulator to merge into oil discharged from a hydraulic pump in which the discharged oil from the hydraulic actuator is increased in pressure using a pressure increasing means such as a pressure increasing cylinder or a pump or even if there is provided no such pressure increasing means. - The present invention relates to a hydraulic control system for a working machine in which hydraulic energy contained in oil discharged from a hydraulic actuator can be recovered and reused. Configurations of the present invention enable a pressure-accumulated oil in an accumulator to be used efficiently without being wasted and a discharge flow rate of the hydraulic pump to be reduced, which results in reliable energy saving. There is also industrial applicability in that a supply flow rate to the hydraulic actuators is stabilized and a smooth operation of the hydraulic actuators is provided because of a precise control over an accumulator merging flow rate from the accumulator to oil discharged from the hydraulic pump.
-
- 8:
- first boom cylinder
- 9:
- second boom cylinder
- 10:
- main pump
- 13:
- regulator
- 15:
- discharge line
- 16:
- merging oil passage
- 27:
- controller
- 52:
- accumulator flow rate control valve
- 59:
- accumulator
- 61:
- pump pressure sensor
- 64:
- accumulator pressure sensor
- 69:
- actuator supply flow rate calculating portion
- 70:
- accumulator flow rate calculating portion
- 71:
- pump flow rate calculating portion
- 72:
- contribution proportion setting portion
- A1 to An:
- Hydraulic actuators
Claims (2)
- A hydraulic control system in a working machine, comprising: an accumulator (59) that pressure-accumulates hydraulic energy contained in oil discharged from a hydraulic actuator (9); a variable-capacity hydraulic pump (10) that serves as a hydraulic supply source for hydraulic actuators (8, 9, Al-An) including at least the hydraulic actuator (9); and a merging oil passage (16) that allows pressure-accumulated oil in the accumulator (59) to merge into oil discharged from the hydraulic pump (10), characterized in that: the hydraulic control system further includes:an accumulator flow rate control valve (52) that controls an accumulator flow rate (Qa) to be merged from the accumulator (59) into the oil discharged from the hydraulic pump (10); and a controller (27) that controls the accumulator flow rate control valve (52) and a discharge flow rate of the hydraulic pump (10), wherein the controller (27):determines a pump flow rate (Qd) according to a pump constant horsepower curve (P-Q curve) that is set according to a pump output signal (Pw) that adjusts an output of the main pump (10), and a discharge pressure (Pp) of the main pump (10), anddetermines a minimum value among the pump flow rate (Qd), a total operation demand flow rate (Qsum (Qsum = Qr + Qr ••• + Qr)) of an operation demand flow rate (Qr) to be demanded by an operation amount of hydraulic actuator operating members, and a maximum flow rate (Qmax) of the hydraulic pump (10), so that the determined minimum value is an actuator supply flow rate (Qc) to be supplied to the hydraulic actuators (8, 9, Al-An), andcontrols a discharge flow rate (Qp) of the hydraulic pump (10) and the accumulator flow rate (Qa) so as to supply the actuator supply flow rate (Qc) corresponding to a total flow rate of the discharge flow rate (Qp) of the hydraulic pump (10)_and the accumulator flow rate (Qa).
- The hydraulic control system in the working machine according to claim 1, in which the controller (27):includes a contribution proportion setting means (72) by which an accumulator contribution proportion (Ra) to be contributed by the accumulator (59) and a pump contribution proportion (Rp) to be contributed by the hydraulic pump (10) of the actuator supply flow rate (Qc) to be supplied to the hydraulic actuators (8, 9, Al-An) are arbitrarily set with an operating means,anddetermines the accumulator flow rate (Qa) to be merged from the accumulator (59) into the oil discharged from the hydraulic pump (10) by multiplying the actuator supply flow rate (Qc) by the accumulator contribution proportion (Ra) if an accumulator pressure (Pa) that is detected by an accumulator pressure detecting means (64) is more than or equal to a predetermined pressure (Pas) at which the accumulator (59) is allowed to release pressurized oil and if the detected accumulator pressure (Ra) is more than or equal to the discharge pressure (Pp) of the hydraulic pump (10).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008271759A JP5354650B2 (en) | 2008-10-22 | 2008-10-22 | Hydraulic control system for work machines |
PCT/JP2009/002414 WO2010047008A1 (en) | 2008-10-22 | 2009-06-01 | Hydraulic control system in working machine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2351937A1 EP2351937A1 (en) | 2011-08-03 |
EP2351937A4 EP2351937A4 (en) | 2014-02-26 |
EP2351937B1 true EP2351937B1 (en) | 2016-08-10 |
Family
ID=42119067
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09821710.2A Not-in-force EP2351937B1 (en) | 2008-10-22 | 2009-06-01 | Hydraulic control system in working machine |
Country Status (5)
Country | Link |
---|---|
US (1) | US8689550B2 (en) |
EP (1) | EP2351937B1 (en) |
JP (1) | JP5354650B2 (en) |
CN (1) | CN102203434B (en) |
WO (1) | WO2010047008A1 (en) |
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JP5574375B2 (en) * | 2010-06-30 | 2014-08-20 | キャタピラー エス エー アール エル | Energy regeneration control circuit and work machine |
US9261115B2 (en) * | 2011-12-09 | 2016-02-16 | Toyota Jidosha Kabushiki Kaisha | Hydraulic control system |
CN102852184B (en) * | 2012-05-04 | 2014-09-17 | 山东理工大学 | Hydraulic control system for loader and control method |
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JP6090781B2 (en) | 2013-01-28 | 2017-03-08 | キャタピラー エス エー アール エル | Engine assist device and work machine |
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JP6529836B2 (en) * | 2015-06-24 | 2019-06-12 | 株式会社神戸製鋼所 | Hydraulic drive and control method thereof |
US20170051763A1 (en) * | 2015-08-19 | 2017-02-23 | Caterpillar Global Mining Equipment Llc | Accumulator Driven Accessories |
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SE542526C2 (en) * | 2015-10-19 | 2020-06-02 | Husqvarna Ab | Energy buffer arrangement and method for remote controlled demolition robot |
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JP6424879B2 (en) * | 2016-11-16 | 2018-11-21 | 株式会社豊田自動織機 | Hydraulic drive of cargo handling vehicle |
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KR102228436B1 (en) * | 2018-03-15 | 2021-03-16 | 히다찌 겐끼 가부시키가이샤 | Construction machinery |
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-
2008
- 2008-10-22 JP JP2008271759A patent/JP5354650B2/en not_active Expired - Fee Related
-
2009
- 2009-06-01 US US13/124,519 patent/US8689550B2/en not_active Expired - Fee Related
- 2009-06-01 CN CN200980140669.8A patent/CN102203434B/en not_active Expired - Fee Related
- 2009-06-01 WO PCT/JP2009/002414 patent/WO2010047008A1/en active Application Filing
- 2009-06-01 EP EP09821710.2A patent/EP2351937B1/en not_active Not-in-force
Also Published As
Publication number | Publication date |
---|---|
WO2010047008A1 (en) | 2010-04-29 |
JP5354650B2 (en) | 2013-11-27 |
EP2351937A1 (en) | 2011-08-03 |
CN102203434A (en) | 2011-09-28 |
US8689550B2 (en) | 2014-04-08 |
US20110197576A1 (en) | 2011-08-18 |
JP2010101365A (en) | 2010-05-06 |
CN102203434B (en) | 2014-04-09 |
EP2351937A4 (en) | 2014-02-26 |
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